JP6654941B2 - Wheel bearing device - Google Patents

Wheel bearing device Download PDF

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Publication number
JP6654941B2
JP6654941B2 JP2016055966A JP2016055966A JP6654941B2 JP 6654941 B2 JP6654941 B2 JP 6654941B2 JP 2016055966 A JP2016055966 A JP 2016055966A JP 2016055966 A JP2016055966 A JP 2016055966A JP 6654941 B2 JP6654941 B2 JP 6654941B2
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Prior art keywords
wheel
bearing device
ring
rolling
damming
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JP2017172604A (en
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雄太 中辻
雄太 中辻
奈都子 永井
奈都子 永井
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NTN Corp
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NTN Corp
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Priority to JP2016055966A priority Critical patent/JP6654941B2/en
Priority to US16/085,375 priority patent/US10343454B2/en
Priority to DE112017001397.6T priority patent/DE112017001397T5/en
Priority to CN201780017909.XA priority patent/CN108779806B/en
Priority to PCT/JP2017/010730 priority patent/WO2017159804A1/en
Publication of JP2017172604A publication Critical patent/JP2017172604A/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
    • B60B35/02—Dead axles, i.e. not transmitting torque
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0005—Hubs with ball bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0047—Hubs characterised by functional integration of other elements
    • B60B27/0068—Hubs characterised by functional integration of other elements the element being a sensor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0073—Hubs characterised by sealing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/723—Shaft end sealing means, e.g. cup-shaped caps or covers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/768—Sealings of ball or roller bearings between relatively stationary parts, i.e. static seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7896—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members with two or more discrete sealings arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/007—Encoders, e.g. parts with a plurality of alternating magnetic poles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2310/00—Manufacturing methods
    • B60B2310/30—Manufacturing methods joining
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Sealing Devices (AREA)
  • Sealing Of Bearings (AREA)

Description

本発明は車輪用軸受装置に関する。   The present invention relates to a bearing device for a wheel.

従来、自動車等の懸架装置において車輪を回転自在に支持し、車輪の回転速度を検出する回転速度検出装置を備えた車輪用軸受装置が知られている。車輪用軸受装置は、車輪に接続されるハブ輪が転動体を介して回転自在に支持されている。また、車輪用軸受装置の回転速度検出装置は、円周方向に異なる磁極が交互に着磁された磁気エンコーダと磁気センサとから構成されている。車輪用軸受装置は、ハブ輪に磁気エンコーダが固定され、ハブ輪とともに回転しない部分に磁気センサが配置されている。車輪用軸受装置は、ハブ輪とともに回転する磁気エンコーダが磁気センサ近傍を通過する際の磁性の変化の間隔からハブ輪に接続される車輪の回転速度を検出することができる。   2. Description of the Related Art Conventionally, there has been known a wheel bearing device provided with a rotation speed detecting device that rotatably supports a wheel in a suspension device of an automobile or the like and detects a rotation speed of the wheel. In the wheel bearing device, a hub wheel connected to the wheel is rotatably supported via a rolling element. Further, the rotation speed detecting device of the wheel bearing device includes a magnetic encoder and magnetic sensors in which different magnetic poles are alternately magnetized in the circumferential direction. In the bearing device for a wheel, a magnetic encoder is fixed to a hub wheel, and a magnetic sensor is disposed in a portion that does not rotate with the hub wheel. The wheel bearing device can detect the rotation speed of the wheel connected to the hub wheel from the interval of the change in magnetism when the magnetic encoder that rotates with the hub wheel passes near the magnetic sensor.

このような車輪用軸受装置において、回転速度検出装置の磁気エンコーダへの飛石等による破損、泥土や磁性体等の付着による誤検出を防止するために磁気エンコーダをカバーによって保護しているものがある。車輪用軸受装置の外輪の開口部を非磁性体のカバーで覆うことで外輪の内部に磁気エンコーダを密閉するものである。このように構成することで、車輪用軸受装置は、磁気エンコーダを飛石や泥土から保護しつつ、磁気センサによって磁気エンコーダの磁性の変化を検出することができる。例えば、特許文献１に記載の如くである。   In such a wheel bearing device, there is one in which a magnetic encoder is protected by a cover in order to prevent damage to the magnetic encoder of the rotation speed detecting device due to flying stones, etc., and to prevent erroneous detection due to adhesion of mud, magnetic material, or the like. . The magnetic encoder is sealed inside the outer ring by covering the opening of the outer ring of the wheel bearing device with a cover made of a non-magnetic material. With this configuration, the bearing device for a wheel can detect a change in magnetism of the magnetic encoder with the magnetic sensor while protecting the magnetic encoder from flying stones and mud. For example, as described in Patent Document 1.

特許文献１に記載のエンコーダ付転がり軸受ユニット（車輪用軸受装置）は、外輪（外方部材）と、ハブ本体（内方部材）と、カバーと、エンコーダとを具備する。外輪の内部には、ハブ本体が転動体を介して回転自在に支持されている。転動体の近傍には、転動体とハブ本体との間、および転動体と外輪との間を潤滑するためのグリースが注入されている。ハブ本体の一側端部には、エンコーダが支持環（支持環）を介して固定されている。エンコーダの検出面と対向する外輪の開口部には、有底円筒状のカバーが嵌合されている。エンコーダ付転がり軸受ユニットは、車輪の懸架装置のナックルに取り付けられるとともに、エンコーダの回転をする図示しない磁気センサがナックルに支持されている。   A rolling bearing unit with an encoder (wheel bearing device) described in Patent Literature 1 includes an outer ring (outer member), a hub body (inner member), a cover, and an encoder. Inside the outer race, a hub body is rotatably supported via rolling elements. Grease for lubricating between the rolling elements and the hub body and between the rolling elements and the outer ring is injected near the rolling elements. An encoder is fixed to one end of the hub body via a support ring (support ring). A bottomed cylindrical cover is fitted into the opening of the outer ring facing the detection surface of the encoder. The rolling bearing unit with the encoder is mounted on a knuckle of a wheel suspension device, and a magnetic sensor (not shown) for rotating the encoder is supported by the knuckle.

カバーは、円筒部（側部）と円盤状の底面である外径側平板部と内径側平板部とが連結板部を介して一体的に形成されている。これにより、エンコーダ付転がり軸受ユニットのカバーは、カバーによって内部にグリースとエンコーダとを封入し、グリース等への泥土や異物の混入を防止するとともに泥土や磁性体等からエンコーダを保護する。しかし、エンコーダ付転がり軸受ユニットには、エンコーダを設置するための空間が転動体から外側（インナー側）に構成されている。このため、転動体の近傍に封入されているグリースが転動体の回転により掻き出されてエンコーダが設置されている空間に流出する可能性がある。従って、エンコーダ付転がり軸受ユニットには、エンコーダが設置されている空間へのグリースの流出量を考慮してグリースを封入する必要があった。   In the cover, a cylindrical portion (side portion) and an outer-diameter-side flat plate portion and an inner-diameter-side flat plate portion which are disc-shaped bottom surfaces are integrally formed via a connecting plate portion. As a result, the cover of the rolling bearing unit with the encoder seals the grease and the encoder inside by the cover, thereby preventing the mud and foreign matter from being mixed into the grease and protecting the encoder from the mud and the magnetic material. However, in the rolling bearing unit with the encoder, a space for installing the encoder is formed outside (the inner side) from the rolling element. For this reason, there is a possibility that the grease sealed in the vicinity of the rolling element is scraped out by the rotation of the rolling element and flows out into the space where the encoder is installed. Therefore, it is necessary to enclose grease in the rolling bearing unit with encoder in consideration of the amount of grease flowing into the space where the encoder is installed.

特開２０１１−２０８７０２号公報JP 2011-208702 A

本発明は以上の如き状況に鑑みてなされたものであり、転動体近傍からのグリースの流出を抑制し、グリースの封入量を低減させることができる車輪用軸受装置の提供を目的とする。   The present invention has been made in view of the above situation, and an object of the present invention is to provide a bearing device for a wheel that can suppress the outflow of grease from the vicinity of a rolling element and reduce the amount of grease enclosed.

即ち、内周に複列の外側転走面が一体に形成された外方部材と、一端部に車輪を取り付けるための車輪取り付けフランジを一体に有し、外周に軸方向に延びる小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に圧入された少なくとも一つの内輪からなり、外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、この内方部材と前記外方部材のそれぞれの転走面間に転動自在に収容された複列の転動体と、内方部材のインナー側の端部に設けられている磁気エンコーダと、磁気エンコーダに対向するように外方部材のインナー側の開口部に嵌合されている有底筒状のカバーと、を備えた車輪用軸受装置において、前記外方部材と内方部材との間に封入されている潤滑剤を前記転動体近傍に保持するため、前記カバーの側部に径方向内側に向かって延びる環状の弾性体からなる外側堰き止め部材が設けられるものである。   That is, an outer member integrally formed with a double row of outer rolling surfaces on the inner periphery, and a wheel mounting flange for attaching a wheel to one end portion, and a small-diameter step portion extending axially on the outer periphery. An inner ring comprising a formed hub wheel and at least one inner ring press-fitted into a small-diameter stepped portion of the hub wheel, and having a double row of inner rolling surfaces formed on an outer periphery thereof and facing the double row of outer rolling surfaces. Member, a plurality of rows of rolling elements rotatably accommodated between respective rolling surfaces of the inner member and the outer member, and a magnetic member provided at an inner end of the inner member. A wheel bearing device comprising: an encoder; and a bottomed tubular cover fitted into an inner opening of the outer member so as to face the magnetic encoder. In order to keep the lubricant enclosed between Outer blocking member consists of an annular elastic member on the side of the serial cover extending radially inward in which is provided.

前記外側堰き止め部材が、前記カバーの側部の軸方向端面であって側部の外周面よりも径方向内側に設けられ、外方部材との接触部が軸方向に突出して形成されるものである。   The outer damming member is provided at an axial end surface of a side portion of the cover and radially inward of an outer peripheral surface of the side portion, and a contact portion with an outer member is formed to protrude in an axial direction. It is.

前記外側堰き止め部材が、前記内方部材のインナー側の端部に嵌合されて前記エンコーダを支持している支持環の嵌合部分と軸方向視で重複するように構成されるものである。   The outer damming member is configured to be fitted to an inner end of the inner member and to overlap with a fitting portion of a support ring supporting the encoder when viewed in the axial direction. .

前記外方部材と内方部材との間に封入されている潤滑剤を転動体近傍に保持するため、前記支持環の嵌合部分の端部の全周から径方向外側に向かって延びる環状の内側堰き止め部材が前記外側堰き止め部材と対向するように設けられるものである。   In order to hold the lubricant sealed between the outer member and the inner member in the vicinity of the rolling element, an annular ring extending radially outward from the entire periphery of the end of the fitting portion of the support ring. The inner damming member is provided so as to face the outer damming member.

前記内側堰き止め部材が、前記支持環の嵌合部分の端部から径方向外側に向かって延びる環状の弾性体からなるものである。   The inner damming member is formed of an annular elastic body extending radially outward from an end of the fitting portion of the support ring.

前記内側堰き止め部材が、前記支持環の嵌合部分の端部を径方向外側に屈曲して形成されるものである。   The inner damming member is formed by bending an end of a fitting portion of the support ring radially outward.

本発明の効果として、以下に示すような効果を奏する。   The present invention has the following effects.

即ち、車輪用軸受装置によれば、弾性体からなる外側堰き止め部材を転動体とカバーとの間に配置することで、転動体の転動により潤滑剤が転動体近傍からカバー側に掻き出されても外側堰き止め部材により堰き止められる。これにより、転動体近傍からのグリースの流出を抑制し、グリースの封入量を低減させることができる。   That is, according to the wheel bearing device, by arranging the outer damming member made of the elastic body between the rolling element and the cover, the lubricant is scraped from the vicinity of the rolling element to the cover side by the rolling of the rolling element. Even if it is done, it is blocked by the outside blocking member. Thereby, the outflow of grease from the vicinity of the rolling elements can be suppressed, and the amount of grease sealed can be reduced.

車輪用軸受装置によれば、潤滑剤が注入される転動体の近傍の空間が小さくなる。また、カバーの嵌合を阻害することなく外方部材とカバーとの隙間がシールされる。これにより、転動体近傍からのグリースの流出を抑制し、グリースの封入量を低減させることができる。   According to the wheel bearing device, the space near the rolling element into which the lubricant is injected is reduced. Further, the gap between the outer member and the cover is sealed without obstructing the fitting of the cover. Thereby, the outflow of grease from the vicinity of the rolling elements can be suppressed, and the amount of grease sealed can be reduced.

車輪用軸受装置によれば、エンコーダを支持している支持環の嵌合部分を利用して潤滑剤が外側堰き止め部材によって構成されている隙間を通過するときの通過抵抗を増大させる。これにより、転動体近傍からのグリースの流出を抑制し、グリースの封入量を低減させることができる。   According to the bearing device for a wheel, the passage resistance when the lubricant passes through the gap formed by the outer dam member is increased by using the fitting portion of the support ring that supports the encoder. Thereby, the outflow of grease from the vicinity of the rolling elements can be suppressed, and the amount of grease sealed can be reduced.

車輪用軸受装置によれば、外側堰き止め部材と内側環堰き止め部材とが近接して設けられることで、外側堰き止め部材と内方部材との隙間部分に外側堰き止め部材と内側環堰き止め部材とによってラビリンスが構成される。これにより、転動体近傍からのグリースの流出を抑制し、グリースの封入量を低減させることができる。   According to the wheel bearing device, the outer damming member and the inner ring damming member are provided close to each other, so that the outer damming member and the inner ring damming are provided in the gap between the outer damming member and the inner member. The member forms a labyrinth. Thereby, the outflow of grease from the vicinity of the rolling elements can be suppressed, and the amount of grease sealed can be reduced.

車輪用軸受装置によれば、内側堰き止め部材に内方部材の回転によって遠心力が加わっても外側堰き止め部材との位置関係が維持される。これにより、転動体近傍からのグリースの流出を抑制し、グリースの封入量を低減させることができる。   According to the wheel bearing device, even if centrifugal force is applied to the inner blocking member by rotation of the inner member, the positional relationship with the outer blocking member is maintained. Thereby, the outflow of grease from the vicinity of the rolling elements can be suppressed, and the amount of grease sealed can be reduced.

車輪用軸受装置の第一実施形態における全体構成を示す斜視図。FIG. 1 is a perspective view showing an overall configuration of a wheel bearing device according to a first embodiment. （ａ）車輪用軸受装置の第一実施形態における全体構成を示す端面図、（ｂ）図２（ａ）におけるＡ部を示す拡大端面図。2A is an end view showing the overall configuration of the wheel bearing device according to the first embodiment, and FIG. 2B is an enlarged end view showing a portion A in FIG. 車輪用軸受装置の第一実施形態におけるカバーの外側堰き止め部材を示す拡大断面図。FIG. 4 is an enlarged cross-sectional view illustrating an outer damming member of a cover in the first embodiment of the wheel bearing device. 車輪用軸受装置の第一実施形態においてカバーが挿入される際の外側堰き止め部材の弾性変形の態様を示す拡大断面図。FIG. 4 is an enlarged cross-sectional view showing a mode of elastic deformation of an outer damming member when a cover is inserted in the first embodiment of the wheel bearing device. 車輪用軸受装置の第一実施形態においてカバーが所定位置に嵌合された状態を示す拡大断面図。FIG. 4 is an enlarged sectional view showing a state in which a cover is fitted to a predetermined position in the first embodiment of the wheel bearing device. 車輪用軸受装置の第一実施形態において潤滑剤が磁気エンコーダ側に掻き出された状態を示す拡大断面図。FIG. 4 is an enlarged cross-sectional view showing a state in which lubricant is scraped out to the magnetic encoder side in the first embodiment of the wheel bearing device. 車輪用軸受装置の第一実施形態での外側堰き止め部材の位置が異なる実施形態において潤滑剤が磁気エンコーダ側に掻き出された状態を示す拡大断面図。FIG. 4 is an enlarged cross-sectional view showing a state in which lubricant is scraped out to the magnetic encoder side in the first embodiment of the wheel bearing device in which the position of the outer blocking member is different. 車輪用軸受装置の第二実施形態における外側堰き止め部材と内側堰き止め部材とを示す拡大断面図。The expanded sectional view showing the outside dam member and the inside dam member in a second embodiment of a bearing device for wheels. 車輪用軸受装置の第二実施形態において潤滑剤が磁気エンコーダ側に掻き出された状態を示す拡大断面図。FIG. 8 is an enlarged cross-sectional view showing a state in which lubricant is scraped out to the magnetic encoder side in the second embodiment of the wheel bearing device. 車輪用軸受装置の第二実施形態での内側堰き止め部材の構成が異なる実施形態を示す拡大断面図。The expanded sectional view showing the embodiment from which the composition of the inner dam member in the second embodiment of the bearing device for wheels differs.

以下に、図１と図２とを用いて、車輪用軸受装置の第一実施形態である車輪用軸受装置１について説明する。   Hereinafter, the wheel bearing device 1 which is the first embodiment of the wheel bearing device will be described with reference to FIGS. 1 and 2.

図１に示すように、車輪用軸受装置１は、自動車等の車両の懸架装置において車輪を回転自在に支持するものである。車輪用軸受装置１は、外輪２、ハブ輪３、内輪４（図２参照）、転動体である二列のボール列５（図２参照）、回転速度検出装置６（図２参照）、支持環８（図２参照）、シール部材１０（図２参照）およびカバー１１を具備する。   As shown in FIG. 1, a wheel bearing device 1 rotatably supports wheels in a suspension system of a vehicle such as an automobile. The wheel bearing device 1 includes an outer ring 2, a hub wheel 3, an inner ring 4 (see FIG. 2), two rows of balls 5 as rolling elements (see FIG. 2), a rotational speed detecting device 6 (see FIG. 2), and a support. A ring 8 (see FIG. 2), a seal member 10 (see FIG. 2), and a cover 11 are provided.

図２（ａ）に示すように、外方部材である外輪２は、ハブ輪３と内輪４とを支持するものである。外輪２は、略円筒状に形成され、Ｓ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で構成されている。外輪２の内周面には、周方向に環状の外側転走面２ａが一側（インナー側）と他側（アウター側）とに平行になるように形成されている。各外側転走面２ａ・２ａには、高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲とする硬化層が形成されている。外輪２の一側端部（インナー側）には、カバー１１が嵌合可能な一側開口部２ｂが形成されている。一側開口部２ｂには、カバー１１の嵌合位置を決めるための段差部２ｃが形成されている（図２（ｂ）参照）。外輪２の他側端部（アウター側）には、シール部材１０が嵌合可能な他側開口部２ｄが形成されている。外輪２の外周面には、図示しない懸架装置のナックルに取り付けるための車体取り付けフランジ２ｅが一体に形成されている。   As shown in FIG. 2A, an outer ring 2 serving as an outer member supports a hub wheel 3 and an inner ring 4. The outer ring 2 is formed in a substantially cylindrical shape, and is made of a medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C. On the inner peripheral surface of the outer ring 2, an outer rolling surface 2a that is annular in the circumferential direction is formed so as to be parallel to one side (inner side) and the other side (outer side). A hardened layer having a surface hardness in the range of 58 to 64 HRC is formed on each of the outer rolling surfaces 2a by induction hardening. One end (inner side) of the outer ring 2 is formed with a one-side opening 2b into which the cover 11 can be fitted. The one-side opening 2b is formed with a step 2c for determining the fitting position of the cover 11 (see FIG. 2B). The other end (outer side) of the outer ring 2 is formed with another opening 2d into which the seal member 10 can be fitted. On the outer peripheral surface of the outer race 2, a vehicle body mounting flange 2e for mounting to a knuckle of a suspension device (not shown) is integrally formed.

内方部材の一部であるハブ輪３は、図示しない車両の車輪を回転自在に支持するものである。ハブ輪３は、有底円筒状に形成され、Ｓ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で構成されている。ハブ輪３の一側端部（インナー側）には、外周面に縮径された小径段部３ａが形成されている。ハブ輪３の一端部である他側端部（アウター側）には、車輪を取り付けるための車輪取り付けフランジ３ｂが一体的に形成されている。車輪取り付けフランジ３ｂには、円周等配位置にハブボルト３ｃが設けられている。また、ハブ輪３の他側の外周面には、周方向に環状の内側転走面３ｄが形成されている。   The hub wheel 3 as a part of the inner member rotatably supports a vehicle wheel (not shown). The hub wheel 3 is formed in a cylindrical shape with a bottom and is made of medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C. At one end (inner side) of the hub wheel 3, a small-diameter stepped portion 3a whose diameter is reduced is formed on the outer peripheral surface. A wheel mounting flange 3b for mounting a wheel is integrally formed on the other end (outer side), which is one end of the hub wheel 3. Hub bolts 3c are provided on the wheel mounting flange 3b at circumferentially equal positions. On the other outer peripheral surface of the hub wheel 3, an annular inner rolling surface 3d is formed in the circumferential direction.

ハブ輪３の一側端部の小径段部３ａは、内方部材の一部である内輪４が圧入されている。ハブ輪３と内輪４とから内方部材が構成されている。内輪４は、ＳＵＪ２等の高炭素クロム軸受鋼からなり、ズブ焼入れにより芯部まで５８〜６４ＨＲＣの範囲で硬化処理されている。内輪４の外周面には、周方向に環状の内側転走面４ａが形成されている。内輪４は、ハブ輪３の一側端が径方向の外側に向かって塑性変形（加締め）されることで所定の予圧が付与された状態でハブ輪３の一側端部に一体的に固定されている。つまり、ハブ輪３の一側には、内輪４によって内側転走面４ａが構成されている。ハブ輪３は、一側の小径段部３ａから他側の内側転走面３ｄまでを高周波焼入れにより表面硬さを５８〜６４ＨＲＣの範囲に硬化処理されている。これにより、ハブ輪３は、車輪取り付けフランジ３ｂに付加される回転曲げ荷重に対して充分な機械的強度を有し、ハブ輪３の耐久性が向上する。なお、一側端の加締め部分は鍛造加工後の表面硬さのままである。ハブ輪３は、一側端部の内輪４に形成されている内側転走面４ａが外輪２の一側の外側転走面２ａに対向し、他側に形成されている内側転走面３ｄが外輪２の他側の外側転走面２ａに対向するように配置されている。   An inner ring 4 which is a part of an inner member is press-fitted into a small-diameter stepped portion 3 a at one end of the hub wheel 3. An inner member is composed of the hub wheel 3 and the inner ring 4. The inner ring 4 is made of high carbon chromium bearing steel such as SUJ2, and has been hardened to 58 to 64 HRC up to the core by subbing quenching. On the outer peripheral surface of the inner ring 4, an annular inner rolling surface 4a is formed in the circumferential direction. The inner ring 4 is integrally formed with one end of the hub wheel 3 in a state where a predetermined preload is applied by plastically deforming (caulking) one end of the hub wheel 3 toward the outside in the radial direction. Fixed. That is, on one side of the hub wheel 3, the inner race surface 4 forms the inner rolling surface 4a. The hub wheel 3 is hardened by induction hardening from the small-diameter stepped portion 3a on one side to the inner rolling surface 3d on the other side to have a surface hardness of 58 to 64 HRC. Thereby, the hub wheel 3 has sufficient mechanical strength against the rotating bending load applied to the wheel mounting flange 3b, and the durability of the hub wheel 3 is improved. The crimped portion at one end remains the surface hardness after forging. In the hub wheel 3, an inner rolling surface 4a formed on the inner race 4 at one end is opposed to an outer rolling surface 2a on one side of the outer race 2, and an inner rolling surface 3d formed on the other side. Are disposed so as to face the outer rolling surface 2a on the other side of the outer ring 2.

転動体である二列のボール列５は、ハブ輪３を回転自在に支持するものである。二列のボール列５は、複数のボールが保持器によって環状に保持されている。二列のボール列５は、ＳＵＪ２等の高炭素クロム軸受鋼からなり、ズブ焼入れにより芯部まで５８〜６４ＨＲＣの範囲で硬化処理されている。二列のボール列５のうち一方のボール列５は、内輪４に形成されている内側転走面４ａと、それに対向している外輪２の一側の外側転走面２ａとの間に転動自在に挟まれている。二列のボール列５のうち他方のボール列５は、ハブ輪３に形成されている内側転走面３ｄと、それに対向している外輪２の他側の外側転走面２ａとの間に転動自在に挟まれている。つまり、二列のボール列５は、外輪２に対してハブ輪３と内輪４とを回転自在に支持している。このように、車輪用軸受装置１は、外輪２とハブ輪３と内輪４と二列のボール列５とから複列アンギュラ玉軸受が構成されている。なお、本実施形態において、車輪用軸受装置１には、複列アンギュラ玉軸受が構成されているがこれに限定されるものではなく、複列円錐ころ軸受等で構成されていても良い。   The two ball rows 5 as rolling elements support the hub wheel 3 rotatably. In the two rows of balls 5, a plurality of balls are annularly held by a holder. The two ball rows 5 are made of high carbon chromium bearing steel such as SUJ2, and have been hardened to the core by subbing quenching in the range of 58 to 64 HRC. One of the two ball rows 5 is arranged between an inner rolling surface 4a formed on the inner race 4 and an outer rolling surface 2a on one side of the outer race 2 opposed thereto. It is sandwiched freely. The other ball row 5 of the two rows of ball rows 5 is located between the inner rolling surface 3d formed on the hub wheel 3 and the outer rolling surface 2a on the other side of the outer wheel 2 opposed thereto. Rolled freely. That is, the two ball rows 5 rotatably support the hub wheel 3 and the inner ring 4 with respect to the outer ring 2. Thus, in the wheel bearing device 1, a double-row angular ball bearing is configured by the outer ring 2, the hub wheel 3, the inner ring 4, and the two rows of ball rows 5. In the present embodiment, a double-row angular contact ball bearing is formed in the wheel bearing device 1, but the present invention is not limited to this, and a double-row tapered roller bearing or the like may be used.

回転速度検出装置６は、ハブ輪３と内輪４との軸回りの回転速度を検出するものである。回転速度検出装置６は、磁気エンコーダ７と磁気センサ９とを具備するエンコーダから構成されている。   The rotation speed detecting device 6 detects the rotation speed of the hub wheel 3 and the inner ring 4 around the axis. The rotation speed detecting device 6 includes an encoder including a magnetic encoder 7 and a magnetic sensor 9.

図２（ｂ）に示すように、磁気エンコーダ７は、フェライト等の磁性紛体が混入された合成ゴムが環状に形成され、周方向に等ピッチで磁極Ｎと磁極Ｓとに着磁されたものである。磁気エンコーダ７は、支持環８の鍔部８ａに加硫接着によって一体に接合されている。磁気エンコーダ７は、内輪４に嵌合されている支持環８を介して外輪２の一側開口部２ｂに配置されている。すなわち、磁気エンコーダ７は、支持環８および内輪４を介してハブ輪３と一体的に回転可能に構成されている。   As shown in FIG. 2 (b), the magnetic encoder 7 is formed by forming a synthetic rubber in which a magnetic powder such as ferrite is mixed into an annular shape, and magnetizing the magnetic poles N and S at equal pitches in the circumferential direction. It is. The magnetic encoder 7 is integrally joined to the flange 8a of the support ring 8 by vulcanization bonding. The magnetic encoder 7 is disposed at one opening 2 b of the outer ring 2 via a support ring 8 fitted to the inner ring 4. That is, the magnetic encoder 7 is configured to be rotatable integrally with the hub wheel 3 via the support ring 8 and the inner ring 4.

支持環８は、磁気エンコーダ７を支持するものである。支持環８は、一側端部に鍔部８ａが形成されている円筒状部材である。鍔部８ａの外径は、他側端部の円筒部８ｂの外径よりも大きく形成されている。支持環８の鍔部８ａには、磁気エンコーダ７が加硫接着によって一体に接合されている。支持環８の円筒部８ｂは、嵌合部分として内輪４に嵌合されている。支持環８は、防錆性の向上と検出精度の安定性の向上のため強磁性体の鋼板、例えば、フェライト系のステンレス鋼鈑（ＪＩＳ規格のＳＵＳ４３０系等）や防錆処理された冷間圧延鋼鈑（ＪＩＳ規格のＳＰＣＣ系等）からプレス加工にて形成されている。なお、本実施形態において支持環８の鍔部８ａは、径方向外側に延びて円筒部８ｂよりも大きい外径に形成されているがこれに限定されるものではなく、径方向内側に延びて円筒部８ｂよりも小さい外径に形成されていてもよい。   The support ring 8 supports the magnetic encoder 7. The support ring 8 is a cylindrical member having a flange 8a formed at one end. The outer diameter of the flange 8a is formed larger than the outer diameter of the cylindrical portion 8b at the other end. The magnetic encoder 7 is integrally joined to the flange 8a of the support ring 8 by vulcanization bonding. The cylindrical portion 8b of the support ring 8 is fitted to the inner race 4 as a fitting portion. The support ring 8 is made of a ferromagnetic steel plate, for example, a ferritic stainless steel plate (such as SUS430 of JIS standard) or a rust-proof cold-rolled plate for improving rust prevention and stability of detection accuracy. It is formed by pressing from a rolled steel sheet (such as JIS standard SPCC). In the present embodiment, the flange portion 8a of the support ring 8 extends radially outward and is formed to have an outer diameter larger than the cylindrical portion 8b, but is not limited to this, and extends radially inward. The outer diameter may be smaller than the cylindrical portion 8b.

図２（ａ）に示すように、磁気センサ９は、磁気エンコーダ７の磁性を検出するものである。磁気センサ９は、センサホルダ１７によってその検出面が磁気エンコーダ７に対向するようにして外輪２や図示しない懸架装置のナックルに取り付けられている。磁気センサ９は、磁気エンコーダ７から所定のエアギャップ（軸方向すきま）になるように配置されている。磁気センサ９は、ハブ輪３と一体的に回転することにより交互に検出面を通過する磁気エンコーダ７の各磁性の通過時間を検出する。   As shown in FIG. 2A, the magnetic sensor 9 detects the magnetism of the magnetic encoder 7. The magnetic sensor 9 is attached to the outer ring 2 or a knuckle of a suspension device (not shown) such that a detection surface thereof faces the magnetic encoder 7 by a sensor holder 17. The magnetic sensor 9 is arranged so as to have a predetermined air gap (clearance in the axial direction) from the magnetic encoder 7. The magnetic sensor 9 detects the passage time of each magnetism of the magnetic encoder 7 that alternately passes through the detection surface by rotating integrally with the hub wheel 3.

シール部材１０は、外輪２とハブ輪３との隙間を塞ぐものである。シール部材１０はニトリルゴム等の合成ゴムからなり、加硫接着によって略円筒状に形成された支持環８に一体に接合されている。シール部材１０は、内側に複数のリップが形成されている。シール部材１０は、外輪２の他側開口部２ｄ（アウター側）に円筒部８ｂが嵌合され、ハブ輪３の外周面に複数のリップが接触している。シール部材１０のリップは、ハブ輪３の外周面とリップとの間に形成されている油膜を介して摺動可能に構成されている。これにより、シール部材１０は、軸受内部のグリースｇｒを密閉し、外部からの雨水やダスト等の侵入を防止する。   The seal member 10 closes a gap between the outer ring 2 and the hub wheel 3. The seal member 10 is made of synthetic rubber such as nitrile rubber and is integrally joined to a substantially cylindrical support ring 8 by vulcanization bonding. The seal member 10 has a plurality of lips formed inside. In the seal member 10, the cylindrical portion 8 b is fitted in the other opening 2 d (outer side) of the outer ring 2, and a plurality of lips are in contact with the outer peripheral surface of the hub wheel 3. The lip of the seal member 10 is configured to be slidable via an oil film formed between the outer peripheral surface of the hub wheel 3 and the lip. Thus, the seal member 10 seals the grease gr inside the bearing, and prevents rainwater, dust, and the like from entering from outside.

図２（ｂ）に示すように、カバー１１は、外輪２の一側（インナー側）開口部２ｂを塞いで磁気エンコーダ７を保護するものである。カバー１１は、プレス加工によって有底円筒状に形成され、非磁性のオーステナイト系ステンレス鋼鈑（ＪＩＳ規格のＳＵＳ３０４系等）から構成されている。カバー１１は、円筒状の側部１１ａと中央部が突出した円盤状の底部１１ｂとが一体的に連結されている。側部１１ａは、外輪２の一側開口部２ｂの内径よりも僅かに大きい外径に形成されている。側部１１ａの軸方向端部は、全周に渡って径方向内側に向かうテーパ状に屈曲された外側接着部１１ｃが形成されている。外側接着部１１ｃには、弾性体であるニトリルゴム等の合成ゴム板からなる環状の外側堰き止め部材１１ｄが加硫接着によって一体的に設けられている。外側堰き止め部材１１ｄは、外側接着部１１ｃの全周から径方向内側に向かって延びるように設けられている。   As shown in FIG. 2B, the cover 11 protects the magnetic encoder 7 by closing one side (inner side) opening 2 b of the outer ring 2. The cover 11 is formed into a cylindrical shape with a bottom by press working, and is made of a nonmagnetic austenitic stainless steel plate (such as SUS304 based on JIS). In the cover 11, a cylindrical side part 11a and a disk-shaped bottom part 11b with a central part protruding are integrally connected. The side portion 11a is formed to have an outer diameter slightly larger than the inner diameter of the one side opening 2b of the outer ring 2. At the axial end of the side portion 11a, an outer adhesive portion 11c is formed which is bent in a tapered shape toward the radially inner side over the entire circumference. An annular outer damming member 11d made of a synthetic rubber plate such as nitrile rubber as an elastic body is integrally provided on the outer bonding portion 11c by vulcanization bonding. The outer damming member 11d is provided so as to extend radially inward from the entire periphery of the outer bonding portion 11c.

カバー１１は、外輪２の一側開口部２ｂに側部１１ａが嵌合されている。カバー１１は、側部１１ａが一側開口部２ｂに挿入される。カバー１１は、側部１１ａの軸方向端面が一側開口部２ｂの段差部２ｃに接触することで所定の位置に嵌合されている。所定の位置に嵌合されたカバー１１の外側堰き止め部材１１ｄは、ボール列５の近傍でボール列５と磁気エンコーダ７との間を仕切るように配置されている。カバー１１は、側部１１ａが外輪２に嵌合されることで外輪２の一側開口部２ｂを塞いでいる。これにより、カバー１１は、一側開口部２ｂ近傍に配置されているボール列５の近傍に注入されているグリースｇｒを外輪２の内部に封入するとともに、磁気エンコーダ７を保護している。なお、外側堰き止め部材１１ｄは、圧入時の作業性や素材の性質等から、圧入時の損傷を防止するために変形代Ｇの圧縮率が４５％未満になるように形成されている。   The cover 11 has a side portion 11 a fitted into one side opening 2 b of the outer ring 2. The cover 11 has the side portion 11a inserted into the one-side opening 2b. The cover 11 is fitted in a predetermined position by the axial end face of the side portion 11a contacting the step 2c of the one side opening 2b. The outer damming member 11 d of the cover 11 fitted at a predetermined position is arranged so as to partition between the ball row 5 and the magnetic encoder 7 near the ball row 5. The cover 11 covers the one-side opening 2 b of the outer ring 2 by fitting the side portion 11 a to the outer ring 2. Thus, the cover 11 seals the grease gr injected near the ball row 5 arranged near the one-side opening 2b inside the outer ring 2 and protects the magnetic encoder 7. The outer damming member 11d is formed so that the compression ratio of the deformation allowance G is less than 45% in order to prevent damage at the time of press-fitting due to workability at the time of press-fitting and the properties of the material.

このように構成される車輪用軸受装置１は、外輪２とハブ輪３と内輪４と二列のボール列５とから複列アンギュラ玉軸受が構成され、ハブ輪３が二列のボール列５を介して外輪２に回転自在に支持されている。また、車輪用軸受装置１は、磁気エンコーダ７がハブ輪３に固定され、カバー１１によって保護されている。車輪用軸受装置１は、ハブ輪３と一体的に回転する磁気エンコーダ７の磁性の変化を外輪２に固定されている磁気センサ９により検出する。   In the thus configured wheel bearing device 1, a double-row angular ball bearing is constituted by the outer ring 2, the hub wheel 3, the inner ring 4, and the two rows of ball rows 5, and the hub wheel 3 has two rows of ball rows 5. And is rotatably supported by the outer race 2 through the shaft. In the wheel bearing device 1, the magnetic encoder 7 is fixed to the hub wheel 3 and protected by the cover 11. The wheel bearing device 1 detects a change in magnetism of a magnetic encoder 7 that rotates integrally with the hub wheel 3 by a magnetic sensor 9 fixed to the outer ring 2.

次に、図３から図６を用いて、カバー１１の外側堰き止め部材１１ｄについて詳細に説明する。   Next, the outer damming member 11d of the cover 11 will be described in detail with reference to FIGS.

図３に示すように、外側堰き止め部材１１ｄには、外側接着部１１ｃのテーパ部分の全周にわたって合成ゴムが注入された環状のラジアルシール部１１ｅが一体に形成されている。さらに、外側堰き止め部材１１ｄには、全周にわたって軸方向に突出した環状のアキシアルシール部１１ｆが一体に形成されている。つまり、ラジアルシール部１１ｅとアキシアルシール部１１ｆとは、外側堰き止め部材１１ｄの一部として一体に形成されている。外側堰き止め部材１１ｄは、その外形を形成しているラジアルシール部１１ｅの外径Ｄ１が側部１１ａの外径Ｄ２よりも小さくなるように形成されている。また、外側堰き止め部材１１ｄは、その内径ｄ１が支持環８の円筒部８ｂの外径Ｄ３よりも小さく、内輪４の外径Ｄ４よりも大きくなるように形成されている。   As shown in FIG. 3, the outer damming member 11d is integrally formed with an annular radial seal portion 11e in which synthetic rubber is injected over the entire periphery of the tapered portion of the outer bonding portion 11c. Further, an annular axial seal portion 11f protruding in the axial direction over the entire circumference is integrally formed on the outer damming member 11d. That is, the radial seal portion 11e and the axial seal portion 11f are integrally formed as a part of the outer damming member 11d. The outer damming member 11d is formed such that the outer diameter D1 of the radial seal portion 11e forming the outer shape is smaller than the outer diameter D2 of the side portion 11a. The outer damming member 11d is formed so that the inner diameter d1 is smaller than the outer diameter D3 of the cylindrical portion 8b of the support ring 8 and larger than the outer diameter D4 of the inner ring 4.

図４に示すように、カバー１１は、外側堰き止め部材１１ｄが設けられている軸方向端部から外輪２の一側開口部２ｂに挿入される（白塗矢印参照）。外側堰き止め部材１１ｄは、磁気エンコーダ７を支持している支持環８の円筒部８ｂの外径よりも小さい内径ｄ１に構成されているため支持環８と干渉するが、弾性変形することによってカバー１１の挿入を阻害することがない（黒塗矢印参照）。側部１１ａが一側開口部２ｂに挿入される際、外側堰き止め部材１１ｄのラジアルシール部１１ｅは、側部１１ａの外径Ｄ２（図３参照）よりも小さい外径Ｄ１（図３参照）に形成されているので一側開口部２ｂの側面に接触しない。このため、ラジアルシール部１１ｅは、カバー１１の挿入時に一側開口部２ｂとの間で摩擦力を発生させたり、接触により損傷したりすることがない。   As shown in FIG. 4, the cover 11 is inserted into one side opening 2 b of the outer ring 2 from an axial end where the outer damming member 11 d is provided (see a white arrow). The outer damming member 11d has an inner diameter d1 smaller than the outer diameter of the cylindrical portion 8b of the support ring 8 supporting the magnetic encoder 7, and thus interferes with the support ring 8. No inhibition of insertion of 11 (see black arrow). When the side portion 11a is inserted into the one side opening 2b, the radial seal portion 11e of the outer damming member 11d has an outer diameter D1 (see FIG. 3) smaller than the outer diameter D2 (see FIG. 3) of the side portion 11a. So that it does not come into contact with the side surface of the one-side opening 2b. Therefore, the radial seal portion 11e does not generate a frictional force with the one-side opening 2b when the cover 11 is inserted, and is not damaged by the contact.

図５に示すように、カバー１１は、側部１１ａの軸方向端部が一側開口部２ｂの段差部２ｃに接触することで所定位置に嵌合される。外側堰き止め部材１１ｄのアキシアルシール部１１ｆは、嵌合時の外力によって段差部２ｃに押圧される。これにより、アキシアルシール部１１ｆと一体に形成されているラジアルシール部１１ｅは、側部１１ａの外周面よりも径方向内側にある状態から径方向外側に向かって弾性変形して一側開口部２ｂの側面に押圧される。つまり、カバー１１が一側開口部２ｂの所定位置に嵌合されることにより、ラジアルシール部１１ｅとアキシアルシール部１１ｆとは、一側開口部２ｂと段差部２ｃとにそれぞれ押圧されて一側開口部２ｂとカバー１１との隙間を塞ぐ。   As shown in FIG. 5, the cover 11 is fitted into a predetermined position when the axial end of the side portion 11a contacts the step 2c of the one-side opening 2b. The axial seal portion 11f of the outer damming member 11d is pressed by the step portion 2c by an external force at the time of fitting. As a result, the radial seal portion 11e formed integrally with the axial seal portion 11f is elastically deformed radially outward from a state radially inward of the outer peripheral surface of the side portion 11a, and is elastically deformed toward the one side opening 2b. Is pressed against the side surface. That is, when the cover 11 is fitted to a predetermined position of the one-side opening 2b, the radial seal portion 11e and the axial seal portion 11f are pressed by the one-side opening 2b and the stepped portion 2c, respectively. The gap between the opening 2b and the cover 11 is closed.

外輪２の一側開口部２ｂの所定位置にカバー１１が嵌合されると、外側堰き止め部材１１ｄは、ボール列５と支持環８の円筒部８ｂの軸方向端との間であって支持環８の円筒部８ｂの軸方向端の近傍に配置される。これにより、グリースｇｒが注入されるボール列５の近傍の空間が小さくなる。また、外側堰き止め部材１１ｄは、支持環８の円筒部８ｂの外径Ｄ３（図３参照）よりも小さく内輪４の外径Ｄ４（図３参照）よりも大きい内径ｄ１（図３参照）に構成されている。つまり、外側堰き止め部材１１ｄは、その内径側端と内輪４の外周面との隙間Ｇ１（以下、単に「内輪４との隙間Ｇ１」と記す）のすべてが軸方向視で支持環８の円筒部８ｂの端面と重複する状態でボール列５と磁気エンコーダ７との間に配置されている。このように配置されることにより、外側堰き止め部材１１ｄは、内輪４との隙間Ｇ１だけでなく外側堰き止め部材１１ｄの側面と支持環８の円筒部８ｂの軸方向端との隙間Ｇ２（以下、単に「支持環８との隙間Ｇ２」と記す）において通過抵抗が生じるように構成されている。   When the cover 11 is fitted to a predetermined position of the one side opening 2b of the outer ring 2, the outer damming member 11d is supported between the ball row 5 and the axial end of the cylindrical portion 8b of the support ring 8 and supported. The ring 8 is arranged near the axial end of the cylindrical portion 8b. Thereby, the space near the ball row 5 into which the grease gr is injected is reduced. The outer damming member 11d has an inner diameter d1 (see FIG. 3) smaller than the outer diameter D3 (see FIG. 3) of the cylindrical portion 8b of the support ring 8 and larger than the outer diameter D4 (see FIG. 3) of the inner ring 4. It is configured. That is, in the outer damming member 11d, all of the gap G1 between the inner diameter side end and the outer peripheral surface of the inner ring 4 (hereinafter, simply referred to as "gap G1 with the inner ring 4") is the cylindrical shape of the support ring 8 when viewed in the axial direction. It is arranged between the ball row 5 and the magnetic encoder 7 so as to overlap the end face of the portion 8b. With such an arrangement, the outer damming member 11d has a gap G1 between the side surface of the outer damming member 11d and the axial end of the cylindrical portion 8b of the support ring 8 (hereinafter referred to as a gap G1). (Hereinafter simply referred to as “gap G2 with support ring 8”).

図６に示すように、ボール列５の転動によりボール列５の近傍に注入されているグリースｇｒが掻き出された場合、カバー１１側（磁気エンコーダ７側）に掻き出されたグリースｇｒは、外側堰き止め部材１１ｄによって堰き止められる。外側堰き止め部材１１ｄに堰き止められたグリースｇｒには、ボール列５の転動による掻き出し圧力Ｐが加わる。グリースｇｒは、掻き出し圧力Ｐによって流動時の抵抗が少ない空間に向かって押し出される。この際、グリースｇｒに加わる掻き出し圧力Ｐが外側堰き止め部材１１ｄの内輪４との隙間Ｇ１および支持環８との隙間Ｇ２をグリースｇｒが通過するために必要な圧力Ｐ１（二点鎖線矢印参照）よりも小さい場合、グリースｇｒは、隙間Ｇ１および隙間Ｇ２を通過できない。従って、隙間Ｇ１と隙間Ｇ２とが所定値以下の場合、グリースｇｒは、各隙間を通過することなくボール列５の近傍に保持される。   As shown in FIG. 6, when the grease gr injected near the ball row 5 is scraped by the rolling of the ball row 5, the grease gr scraped to the cover 11 side (magnetic encoder 7 side) Is blocked by the outer blocking member 11d. The grease gr that is blocked by the outer blocking member 11d receives a scraping pressure P due to the rolling of the ball row 5. The grease gr is pushed out by the scraping pressure P toward a space where the resistance during the flow is small. At this time, the pressure P1 required for the grease gr to pass through the gap G1 with the inner ring 4 and the gap G2 with the support ring 8 of the outer damming member 11d due to the scraping pressure P applied to the grease gr (see the double-dashed arrow). If smaller, the grease gr cannot pass through the gap G1 and the gap G2. Therefore, when the gap G1 and the gap G2 are equal to or smaller than the predetermined value, the grease gr is held near the ball row 5 without passing through each gap.

このように構成される車輪用軸受装置１は、カバー１１の側部１１ａの軸方向端部に合成ゴムからなる外側堰き止め部材１１ｄを設けることで、グリースｇｒの注入量が抑制されるだけでなく、ボール列５の転動によりグリースｇｒがボール列５の近傍からカバー１１側に掻き出されても外側堰き止め部材１１ｄにより堰き止められる。また、車輪用軸受装置１は、外側堰き止め部材１１ｄの内輪４との隙間Ｇ１と支持環８との隙間Ｇ２とをグリースｇｒが通過するために必要な圧力Ｐ１がボール列５の掻き出し圧力Ｐよりも大きくなるように外側堰き止め部材１１ｄを構成することで、グリースｇｒがボール列５の近傍に保持される。これにより、ボール列５の近傍から磁気エンコーダ７側へのグリースｇｒの流出を抑制し、グリースｇｒの封入量を低減させることができる。   The wheel bearing device 1 configured as described above is provided with the outer damming member 11d made of synthetic rubber at the axial end of the side portion 11a of the cover 11, so that the injection amount of the grease gr is suppressed only. In addition, even if the grease gr is scraped from the vicinity of the ball row 5 toward the cover 11 by the rolling of the ball row 5, the grease gr is blocked by the outer blocking member 11d. Further, in the wheel bearing device 1, the pressure P 1 required for the grease gr to pass through the gap G 1 between the outer damming member 11 d and the inner ring 4 and the gap G 2 between the support ring 8 is the scraping pressure P of the ball row 5. The grease gr is held near the ball row 5 by configuring the outer damming member 11d to be larger than the above. Thus, the outflow of grease gr from the vicinity of the ball row 5 to the magnetic encoder 7 side can be suppressed, and the amount of grease gr enclosed can be reduced.

本実施形態の別実施形態として、図７に示すように、外側堰き止め部材１１ｄを、支持環８の円筒部８ｂの外周面上に配置して円筒部８ｂの外周面との間に隙間Ｇ３を構成してもよい。この際、外側堰き止め部材１１ｄは、円筒部８ｂの外周面との隙間Ｇ３をグリースｇｒが通過するために必要な圧力Ｐ２（二点鎖線矢印参照）が掻き出し圧力Ｐよりも大きくなるように構成されている。   As another embodiment of the present embodiment, as shown in FIG. 7, an outer damming member 11d is disposed on the outer peripheral surface of the cylindrical portion 8b of the support ring 8, and a gap G3 is formed between the outer damming member 11d and the outer peripheral surface of the cylindrical portion 8b. May be configured. At this time, the outer damming member 11d is configured such that a pressure P2 (see an arrow indicated by a two-dot chain line) required for the grease gr to pass through the gap G3 with the outer peripheral surface of the cylindrical portion 8b is larger than the scraping pressure P. Have been.

次に、図８と図９とを用いて、車輪用軸受装置の第二実施形態である車輪用軸受装置１２にについて説明する。なお、以下の実施形態に係る車輪用軸受装置１２は、図１から図７に示す車輪用軸受装置１において、車輪用軸受装置１に替えて適用されるものとして、その説明で用いた名称、図番、記号を用いることで、同じものを指すこととし、以下の実施形態において、既に説明した実施形態と同様の点に関してはその具体的説明を省略し、相違する部分を中心に説明する。   Next, a wheel bearing device 12 which is a second embodiment of the wheel bearing device will be described with reference to FIGS. 8 and 9. Note that the wheel bearing device 12 according to the following embodiment is applied to the wheel bearing device 1 shown in FIGS. 1 to 7 in place of the wheel bearing device 1, and the name used in the description, By using the figure numbers and symbols, the same components are indicated, and in the following embodiments, the same points as those in the already described embodiments will not be specifically described, and different portions will be mainly described.

図８に示すように、支持環１３は、磁気エンコーダ７を支持するものである。支持環１３は、一側端部に鍔部１３ａが形成されている円筒状部材である。支持環１３の鍔部１３ａには、磁気エンコーダ７が加硫接着によって一体に接合されている。支持環１３の円筒部１３ｂは、嵌合部分として内輪４に嵌合されている。円筒部１３ｂの軸方向端部は、全周に渡って径方向外側に向かって屈曲された内側接着部１３ｃが形成されている。内側接着部１３ｃには、弾性体であるニトリルゴム等の合成ゴム板からなる環状の内側堰き止め部材１３ｄが加硫接着によって一体的に設けられている。内側堰き止め部材１３ｄは、内側接着部１３ｃの全周から径方向外側に向かって延びるように設けられている。内側堰き止め部材１３ｄは、その外径Ｄ５がカバー１１の外側堰き止め部材１１ｄの内径ｄ１よりも大きくなるように形成されている。内輪４の所定位置に支持環１３が嵌合されると、内側堰き止め部材１３ｄは、ボール列５の近傍に配置される。   As shown in FIG. 8, the support ring 13 supports the magnetic encoder 7. The support ring 13 is a cylindrical member having a flange 13a formed at one end. The magnetic encoder 7 is integrally joined to the flange 13a of the support ring 13 by vulcanization bonding. The cylindrical portion 13b of the support ring 13 is fitted to the inner race 4 as a fitting portion. At the axial end of the cylindrical portion 13b, an inner bonding portion 13c bent radially outward is formed over the entire circumference. An annular inner damming member 13d made of a synthetic rubber plate such as nitrile rubber, which is an elastic body, is integrally provided on the inner bonding portion 13c by vulcanization bonding. The inner damming member 13d is provided so as to extend radially outward from the entire periphery of the inner bonding portion 13c. The inner damming member 13d is formed such that its outer diameter D5 is larger than the inner diameter d1 of the outer damming member 11d of the cover 11. When the support ring 13 is fitted to a predetermined position of the inner race 4, the inner damming member 13 d is arranged near the ball row 5.

次に、図８と図９とを用いて、カバー１１の外側堰き止め部材１１ｄと支持環１３の内側堰き止め部材１３ｄとの関係について詳細に説明する。   Next, the relationship between the outer blocking member 11d of the cover 11 and the inner blocking member 13d of the support ring 13 will be described in detail with reference to FIGS.

図８に示すように、カバー１１は、外輪２の一側開口部２ｂに外側堰き止め部材１１ｄが設けられている側部１１ａの軸方向端部から挿入される（白塗矢印参照）。外側堰き止め部材１１ｄは、支持環１３の内側堰き止め部材１３ｄの外径Ｄ５よりも小さい内径ｄ１に構成されているため内側堰き止め部材１３ｄと干渉するが、互いに弾性変形することによってカバー１１の挿入を阻害することがない。   As shown in FIG. 8, the cover 11 is inserted from the axial end of the side portion 11a where the outer damming member 11d is provided in the one side opening 2b of the outer ring 2 (see the white arrow). Since the outer damming member 11d is configured to have an inner diameter d1 smaller than the outer diameter D5 of the inner damming member 13d of the support ring 13, the outer damming member 11d interferes with the inner damming member 13d. Does not interfere with insertion.

外輪２の一側開口部２ｂの所定位置にカバー１１が嵌合されると、外側堰き止め部材１１ｄは、ボール列５と支持環１３の内側堰き止め部材１３ｄとの間であって内側堰き止め部材１３ｄの近傍に配置される。また、外側堰き止め部材１１ｄの内径ｄ１は、内側堰き止め部材１３ｄの外径Ｄ５よりも小さいので、内輪４との隙間のすべてが軸方向視で内側堰き止め部材１３ｄと重複するように構成されている。さらに、外側堰き止め部材１１ｄと内側堰き止め部材１３ｄとの間には、近接配置によってラビリンスＬａが構成されている。このように配置されることにより、外側堰き止め部材１１ｄは、内側堰き止め部材１３ｄとの間のラビリンスＬａにおいて通過抵抗が生じるように構成されている。   When the cover 11 is fitted to a predetermined position of the one side opening 2b of the outer ring 2, the outer damming member 11d is located between the ball row 5 and the inner damming member 13d of the support ring 13 and is inwardly damped. It is arranged near the member 13d. Further, since the inner diameter d1 of the outer damming member 11d is smaller than the outer diameter D5 of the inner damming member 13d, the entire gap with the inner ring 4 is configured to overlap the inner damming member 13d in the axial direction. ing. Further, a labyrinth La is formed between the outer damming member 11d and the inner damming member 13d by proximity arrangement. With this arrangement, the outer damming member 11d is configured to generate a passage resistance in the labyrinth La between the outer damming member 11d and the inner damming member 13d.

図９に示すように、ボール列５の転動によりボール列５の近傍に注入されているグリースｇｒが掻き出された場合、カバー１１側（磁気エンコーダ７側）に掻き出されたグリースｇｒ（矢印参照）は、外側堰き止め部材１１ｄによって堰き止められる。外側堰き止め部材１１ｄに堰き止められたグリースｇｒには、ボール列５の転動による掻き出し圧力Ｐが加わる。グリースｇｒは、掻き出し圧力Ｐによって流動時の抵抗が少ない空間に向かって押し出される。この際、グリースｇｒに加わる掻き出し圧力Ｐが内側堰き止め部材１３ｄとの間のラビリンスＬａをグリースｇｒが通過するために必要な圧力Ｐ３（二点鎖線矢印参照）よりも小さい場合、グリースｇｒは、外側堰き止め部材１１ｄの内輪４との隙間および内側堰き止め部材１３ｄとの間のラビリンスＬａを通過できない。従って、グリースｇｒは、内側堰き止め部材１３ｄとの間のラビリンスＬａの幅と長さとが所定値以下の場合、ラビリンスＬａを通過することなくボール列５の近傍に保持される。   As shown in FIG. 9, when the grease gr injected near the ball row 5 is scraped by the rolling of the ball row 5, the grease gr (screwed) on the cover 11 side (the magnetic encoder 7 side). (See arrow) is blocked by the outer blocking member 11d. The grease gr that is blocked by the outer blocking member 11d receives a scraping pressure P due to the rolling of the ball row 5. The grease gr is pushed out by the scraping pressure P toward a space where the resistance during the flow is small. At this time, if the scraping pressure P applied to the grease gr is smaller than the pressure P3 (see the two-dot chain line arrow) necessary for the grease gr to pass through the labyrinth La between the grease gr and the inner damming member 13d, the grease gr is The labyrinth La between the outer damming member 11d and the inner ring 4 and the labyrinth La between the inner damping member 13d cannot pass. Therefore, when the width and length of the labyrinth La between the grease gr and the inner dam member 13d are equal to or smaller than a predetermined value, the grease gr is held near the ball row 5 without passing through the labyrinth La.

このように構成される車輪用軸受装置１２は、内側堰き止め部材１３ｄと外側堰き止め部材１１ｄとから構成されるラビリンスＬａとを通過するために必要な圧力Ｐ３がボール列５の掻き出し圧力Ｐよりも大きくなるように外側堰き止め部材１１ｄと内側堰き止め部材１３ｄとを構成することで、グリースｇｒがボール列５の近傍に保持される。これにより、ボール列５の近傍から磁気エンコーダ７側へのグリースｇｒの流出を抑制し、グリースｇｒの封入量を低減させることができる。   In the wheel bearing device 12 configured as described above, the pressure P3 required to pass through the labyrinth La including the inner blocking member 13d and the outer blocking member 11d is higher than the scraping pressure P of the ball row 5. The grease gr is held in the vicinity of the ball row 5 by forming the outer damming member 11d and the inner damming member 13d so that the grease gr becomes larger. Thus, the outflow of grease gr from the vicinity of the ball row 5 to the magnetic encoder 7 side can be suppressed, and the amount of grease gr enclosed can be reduced.

なお、本実施形態において、内側堰き止め部材１３ｄを合成ゴムから構成されているものとして説明したがこれに限定されるものではない。図１０に示すように、支持環１３の円筒部１３ｂ端を径方向外側に屈曲させた内側堰き止め部材１３ｅから構成されてもよい。   In the present embodiment, the inside dam member 13d has been described as being made of synthetic rubber, but is not limited to this. As shown in FIG. 10, the support ring 13 may be formed of an inner damming member 13 e in which the end of the cylindrical portion 13 b is bent radially outward.

以上、本実施形態に係る車輪用軸受装置１・１２は、ハブ輪３の外周にボール列５の内側転走面３ｄが直接形成されている第３世代構造の車輪用軸受装置として説明したがこれに限定されるものではなく、例えば、ハブ輪３に一対の内輪４が圧入固定された内輪回転の第２世代構造であっても良い。また、上述の実施形態は、本発明の代表的な形態を示したに過ぎず、本発明の骨子を逸脱しない範囲で種々変形して実施することができる。   As described above, the wheel bearing devices 1 and 12 according to the present embodiment have been described as the wheel bearing devices of the third generation structure in which the inner rolling surface 3d of the ball row 5 is directly formed on the outer periphery of the hub wheel 3. The present invention is not limited to this. For example, a second generation structure of inner ring rotation in which a pair of inner rings 4 are press-fitted and fixed to the hub wheel 3 may be used. Further, the above-described embodiment merely shows a typical mode of the present invention, and can be variously modified and implemented without departing from the gist of the present invention.

１ 車輪用軸受装置
２ 外輪
２ｂ 一側開口部
３ ハブ輪
４ 内輪
５ ボール列
７ 磁気エンコーダ
１０ シール部材
１１ カバー
１１ａ 側部
１１ｂ 外側堰き止め部材
ｇｒ グリース Reference Signs List 1 wheel bearing device 2 outer ring 2b one side opening 3 hub wheel 4 inner ring 5 ball train 7 magnetic encoder 10 seal member 11 cover 11a side portion 11b outer damming member gr grease

Claims (5)

内周に複列の外側転走面が一体に形成された外方部材と、
一端部に車輪を取り付けるための車輪取り付けフランジを一体に有し、外周に軸方向に延びる小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に圧入された少なくとも一つの内輪からなり、外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、
この内方部材と前記外方部材のそれぞれの転走面間に転動自在に収容された複列の転動体と、
内方部材のインナー側の端部に設けられている磁気エンコーダと、
磁気エンコーダに対向するように外方部材のインナー側の開口部に嵌合されている有底筒状のカバーと、を備えた車輪用軸受装置において、
前記外方部材と内方部材との間に封入されている潤滑剤を前記転動体近傍に保持するため、前記カバーの側部に径方向内側に向かって延びる環状の弾性体からなる外側堰き止め部材が設けられ、
前記外側堰き止め部材が、前記カバーの側部の軸方向端面であって側部の外周面よりも径方向内側に設けられ、外方部材との接触部が軸方向に突出して形成される、
車輪用軸受装置。 An outer member in which a double row of outer rolling surfaces are integrally formed on the inner periphery,
A hub wheel integrally having a wheel mounting flange for mounting a wheel at one end thereof, a small-diameter step portion extending in the axial direction on the outer periphery, and at least one inner ring press-fitted into the small-diameter step portion of the hub wheel. An inner member having a double row inner rolling surface formed on the outer periphery thereof, the double row inner rolling surface being opposed to the double row outer rolling surface;
Double-row rolling elements rotatably accommodated between respective rolling surfaces of the inner member and the outer member,
A magnetic encoder provided at an inner end of the inner member,
A bottomed cylindrical cover fitted to the inner-side opening of the outer member so as to face the magnetic encoder;
Outer dam made of a ring-shaped elastic body extending radially inward on the side of the cover in order to hold the lubricant sealed between the outer member and the inner member near the rolling element. A member is provided ,
The outer damming member is provided on the axial end surface of the side portion of the cover and radially inward of the outer peripheral surface of the side portion, and a contact portion with the outer member is formed to protrude in the axial direction.
Bearing device for wheels. 前記外側堰き止め部材が、前記内方部材のインナー側の端部に嵌合されて前記エンコーダを支持している支持環の嵌合部分と軸方向視で重複するように構成される、
請求項１に記載の車輪用軸受装置。 The outer damming member is configured to be axially overlapped with a fitting portion of a support ring that supports the encoder by being fitted to an inner end of the inner member ,
The wheel bearing device according to claim 1 . 前記外方部材と内方部材との間に封入されている潤滑剤を転動体近傍に保持するため、前記支持環の嵌合部分の端部の全周から径方向外側に向かって延びる環状の内側堰き止め部材が前記外側堰き止め部材と対向するように設けられる、
請求項１または請求項２に記載の車輪用軸受装置。 In order to hold the lubricant sealed between the outer member and the inner member in the vicinity of the rolling element, an annular ring extending radially outward from the entire periphery of the end of the fitting portion of the support ring is provided. An inner damming member is provided so as to face the outer damming member ,
The wheel bearing device according to claim 1 or 2 . 前記内側堰き止め部材が、前記支持環の嵌合部分の端部から径方向外側に向かって延びる環状の弾性体からなる、
請求項３に記載の車輪用軸受装置。 The inner damming member is formed of an annular elastic body extending radially outward from an end of the fitting portion of the support ring ,
The wheel bearing device according to claim 3 . 前記内側堰き止め部材が、前記支持環の嵌合部分の端部を径方向外側に屈曲して形成される、
請求項３に記載の車輪用軸受装置。 The inner damming member is formed by bending an end of a fitting portion of the support ring radially outward ,
The wheel bearing device according to claim 3 .
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